Hydraulic device for controlling the feed and stop position of a machine element in cutting, sawing and slicing machines



Oct. 14, 1958 R. LE BRUSQUE 2,855,752

. STOP posmon HYDRAULIC DEVICE FOR CONTROLLING THE FEED AND OF A MACHINE ELEMENT IN CUTTING, SAWING AND SLICING MACHINES Filed Oct. 18, 1956 8 She'ets-Sheet 1 Oct. 14, 1958 R. LE' BRUSQUE HYDRAULIC DEVICE FOR CONTROLLING THE FEED AND STOP POSITION OF A MACHINE ELEMENT IN CUTTING, SAWING AND SLICING MACHINES Filed Oct. 18, 1956 8 Sheets-Sheet 2 E Q Q Oct-14; 1958 v R. LE BRUSQUE 2,855,752

HYDRAULIC DEVICE FOR CONTROLLING THE FEED AND STOP POSITION OF A MACHINE ELEMENT IN CUTTING, SAWING AND SLICING MACHINES Filed Oct. '18. 1956 8 Sheets-Sheet 3 a as K n Oct. 14, 1958 R. LE BRUSQUE v 2,8

TROLL-INC THE FEED AND STOP P0 OF A MACHINE ELEMENT IN CUTTING, SAWING SITION HYDRAULIC DEVICE FOR CON AND SLICING MACHINES 8 Sheets-Sheet 4 Filed Oct. 18, 1956 2,855,752 ND STOP POSITION 8 Sheets-Sheet 5 R. LE BRUSQUE DEVICE FOR CONTROLLING THE FEED A Oct. 14, 1958 HYDRAULIC OF A MACHINE ELEMENT IN CUTTING, SAWING AND SLICING MACHINES Filed Oct. 18, 1956 FAsT APP/20c 51.0w APP HYDRAULIC DEVICE FOR CONTROLLING THE FEED AND STOP POSITION OF A MACHINE ELEMENT IN CUTTING, SAWING AND SLICING MACHINES Filed Oct. 18, 1956' 8 Sheets-Sheet 6 Oct. 14, 1958 R. LE BRUSQUE 2,855,752

STAND STILL 5LOW Pen/21v Oct. 14, 1958 R. u: BRUSQUE 2,855,752

HYDRAULIC DEVICE FOR CONTROLLING THE FEED AND STOP POSITION OF A MACHINE ELEMENT IN CUTTING, SAWING AND SLICING MACHINES Filed Oct. 18. 1956 8 Sheets-Sheet '7 TI TI I17 I40 07 la flap Rake. Flqev Ra id Rate Clutch. hut and 'llz traclfm, flux'lliarj Central Return Control l'nd xl'na Oct. 14, 1958 R. LE BRUSQUE 2,855,752

HYDRAULIC DEVICE FOR CONTROLLING THE FEED AND STOP POSITION OF A MACHINE ELEMENT IN CUTTING, SAWING I AND SLICING MACHINES Filed Oct. 18, 1956 8 Sheets-Sheet 8 IIYDRAULIC DEVICE FOR CONTROLLING THE FEED AND STOP POSITION OF A MACHINE ELEMENT IN CUTTING, SAWING AND SLICING MACHINES The present invention relates to a hydraulic device for driving and controlling, as regards both speed and position, the movements of a machine part or of a material to be worked in a machine where great accuracy is required as to exact end positioning of the part or material. The invention is described hereinafter in its particular application to the rear stack-register of a paper guillotine, but it is to be understood that the hydraulic device of the invention is just as readily applicable to presses, saws, millers or slicers, and that a paper guillotine has been selected merely as one example of a machine wherein it is necessary to provide rapid forward and return movements in conjunction with 'slow forward movements of a register to move a stack of paper sheets to an accurately determined stop position at which the stack is worked. I s

More particularly the device permits the displacement of the register step by step in order to carry out a whole series of regular or irregular cuts on a same paper stack in accordance with one or more predetermined programs for which the machine can be set.

There exist a number of known devices for effecting the movements of the register of a paper guillotine. oldest ones with so-called mechanical drive cannot achieve the accuracy demanded by the users of these machines.

It is known that these devices permit, for example, to carry out cuts of regular and repetitive magnitude, but

the unavoidable inaccuracy of the mechanisms which determine the magnitude of the forward step is multiplied by the number of cuts, and the final result counted over the total length of the ream to be cut is found to be affected by this amount.

These mechanical devices cannot achieve the versatility required for rational working conditions, such'as in mass production and it is well known that for completely cutting 01f the four faces of a paper stack toa given size the operator must carry out manipulations of the stack which are excessive both as regards number and magnitude.

Furthermore the known mechanical devices are;not

readily adjustable as to the magnitude of the deceleration of the forward step at the end of each movement of the register. Owing to this fact it is very diificult to maintain the accuracy of stopping at a constant value regardless of the nature of the products to be cut.' It is well known in this connection that the coefficient of friction on the work table of these various paper products presents The However they do United States Patent p l C 2,855,752

would be desirable. Moreover in the known hydraulic devices of this kind, the control of the rate of forward movement required, on the one hand, by the differences in the force for moving the register and, on the other hand, by the unavoidable difference of the viscosity of the oil with varying temperature has been achieved only by systems of hydraulic valves, s0-called constant pressure or constant flow valves controlled by the variations in pressure of the circuit, but independently of the forward movement of the register. All these control systems offer the disadvantage of responding only with a certain delay which makes impossible any accuracy of the forward movement; finally they can function correctly only at very low speeds.

One object of the invention is to provide a hydraulic control device which permits to control the forward movement of the register in a paper guillotine with the same accuracy as devices with mechanical drive, while preserving the power and smoothness inherent to hydraulic devices, and to attain moreover an accuracy in coming to a standstill at the end of a stroke far superior to that of ordinary hydraulic devices.

Another object of the invention is to control the movement of the register in a paper guillotine by means of a hydraulic device of known type actually used solely as a precision copying device on machine tools. This kind of device is described in Patents Nos. 2,592,812 and 2,601,- 157.

The present invention is characterised substantially by the provision of a hydraulic circuit wherein the fiuid is in permanent circulation, the movements of the register being controlled continuously by the calibration of one or two orifices provided in the fluid circuits, this calibration modifying the pressures of the fluid on the two faces of a piston driving the register. The member controlling this calibration is constituted by a feelervalve movable with a bar or barrel supporting a series of abut ments or stops and sliding freely and axially in end guides. This axial movement permits the abutments or stops carried by the barrel to be constantly drawn into or maintained in contact with a reference finger, movable along a ruler, but always in fixed connection with the register of the paper guillotine.

According to the present invention this feeler valve co-operates with a flank of the reference finger controlled in its movements by the forward movement of the register. It follows therefrom that any error in the position chosen for the register is transmitted invariably as a modification of the normal value of the reaction exercised by the reference finger on the feeler and, therefore, as a slight displacement of the feeler which consequently modifies the distribution of fluid in such a manner as to correct the position of the register by the amount required.

The device according to the invention comprises a mechanism for automatically raising the reference finger in order to effect rapid stroke movements of the register in both directions, in such a manner as to carry out all the conceivable combinations of the working cycle.

The programming of a working cycle is made easier by the possibility of setting on the barrel a series of dogs or stops forming multiple abutments. Moreover, by puting into play a device for the partial and automatic oscillation of the barrel, it is advantageous to combine two or more of the small abutment stops into a multiple dog in order to carry out the more complicated working cycles.

Finally with the object of providing a machine for universal applicability suitable both for large and small production, the device according to the invention can be Patented 0st. 14, less.

combined advantageously with clutch devices permitting manual control for the accurate adjustment of the position of the finger, with or without an abutment, as well as accelerated movements, particularly a rapid forward or return movement of the register.

The accompanying. drawings show by. way. of example but" not] oflimifation. an embodiment'of the ir venti'og as'applied'to'apaper. guillotine? i "Figures 1.,2 and"3. Show three external views. offthe: paper guillotine prbvidedwitha l iydraulici drive and con; trol of the register wherein Figure 1 is. a frontelevation from the operating side, Figure Z is aside elevation, with. part-section. of the drivingicylinder for theregi ster, and Figure 3 is a pla n view showing particularly the..co inec;.. tion of the register with the finger by an endless, band,

Figuref i', is'ajgene ral viewof a follow-upmeans for theh'ydraulic contest device. i V

Figured is a transverse section. on. the line V-V of the abutment barrel represented in Figurefh Figures 6 and 7 show a controlcam; for the rapid return, ofthe register in its, two positions of operation,

Figure 8 shows a detail of afratchet wheel imparting a partial rotary movement. to the abutment barrel.

Figure' 9 shows thedriving pawl of the said ratchet wheel, in a disengaged position.

Figures 10 and'll show a control cam for the partial rotary movement of thebarrel in its two positions.

Figures l2and 13 showja detail of the indexing mechanism for thepar tialrotary movement of the barrel.

Figure 14 is an elevation of the manual control mechae nism from'the operators side.

: Figure 15 is a transverse section on theline XYeX V ofFigurel L' Figure l6.is,atransversesection on the line XVI-XVI of Figure 14 through the axis of the hand controlwhcel.

' Figuresl7 and 18 andl9 show the variousa'xialposr tionsoftheaxle of the hand wheel for the, manual con-.. trol of the rapid forward and return movements, and Figure 19 s howsthe samefor automatic cycle operation.

' FiguresZO, 21 22, 23 and 24 are diagra ms offthe hydraulic circuits for defining all the movements of the register. i i

Figure 25 is a wiringdiagram of the electrical circuits of allthe electromagnets.

Figure 26 is an example; of .the arrangement of a series of stops on the abutment barrel for the definition of a simple cycle.

Figures 27 and 28 show an-exarnplein front'and end views of the juxtaposition of two series of stops or multiple dogs on two adjacentvlines of the abutment barrel for the definition of ajcomplex working cycle.

As seen in Figures 1, 2 and}, the paper guillotine to which the hydraulic deviceaccording to the present invention is applied, is of the usual I. type, and the rear register performs the function usually allotted thereto in that sort of machine.

The machine comprises mainly an upright base Lwhich supports a table 2 on which is placed thestack of the material to be cut. A rear register 3 slides upon the. table 2 and is provided with a toothed rack/1, with its teeth pointing downwardly, which; passes through a slot, Zq provided along the gtable 2. The register Slhas an upstanding bracket 5. i i

A cylinder 6 is fixed below the table Zand has apiston 7 slidable therein which at its end carries apinion 8 in mesh with a toothed rack 9 fixedly attached to the table 2 and at the same time with the said toothed rack 4 fixedly attached to the rear registerfi, Thus any movem'ent of the piston 7 produces tw ice that movement pf the rear register 3.

In certain cases and solely for economyof space, the pinion 8 may be replaced by a couple of differential. pinions or may even be. abolished, and .in this case, the piston 7 is attached directly to .the rear register e upper aske f thrssrt si t rfii arpeted;

by an endless steel band or cable passing over guide pulleys 11 to mounted on the frame 1 to a slider 16 moving on a track 17 also fixed to the frame.

In certain cases which will be dealt with hereinafter the guide pulley 11 may be zreplaced by an assembly as illustrated in Figures 14 and 15.

Parallel to the track 1'7. of the slider there is positioned a function drum program bar or barrel 18 which may e m ulded. w t a ce ta n. numbe f; t m able s ops.

abutments. or dogsesuchas. 19,, 21 and 22 fixed in appropriate grooves.

The barrel 18 is carried freely at one of its ends bya casing 23 containing a; feeler or control valve 24, and at its other end by 'a support containing a control device. illustrated. in. Figures 4. and 6 to 13.

e 16.. Qar es. at h@. l.-. of. rm. a. r e 27 which moves in front of a graduated scale 28, fixed on the uprights of theframe, and. extending parallel to the track 17.

The. lide 16; co p ses. al o a. t e h m illustratedin Figured.

Under the table, at the. back of the, machine, there is arranged ahydraulic supply unit comprising a reservoir 29, a pumpandahydraulic distributor 31. The pipes 32, 33f and-3 4; connect the hydraulic supply unit to the cylinder 6 and to the. casing 23 .ofthe control valve 24.

The ensuing description will explain the operation of the hydraulic device for. actuating the rear register as well as, the. operation, of I the follow-up device for the y ta lie ir u it a ha, ay s o tt e i ma c. operation of the whole machine,

R ferr n o u s. l e e that the. pump 30 sucks in through, the pipe the oil con;

-.pressure desired, and a pipe 40,.returns;theexcessoil to T e Wa e ster-U p nss s th r a' i he directly Orby e fttr nst issicns. nd? enl rg or reducingthe length of stroke.;

Thus the rear register is operat-ed by-thepiston 7, the

movement of-which corresponds to the;directi on, to the speed and to therateof fiowof the ,fluid ofth'e-hydraulic sy m s ribe -h r inaft w th fe enc q'. s told.

H ydraulic. system The pump 30 operates permanently in such a manner that the pressure andthefiuidputput are determinedby the throttling member 38, the distributor. 31, the safetyvalve 39-. or the control valve 24 as the case may he.

a ist ibu ma a ctuat d i any es d-m n:

ner but in a-preferredform it .is operated alternately by two-electromagnets :as will beexplained later;

The; controlyalve; 24. is operativelyconnected to the barreldfi, urged-by the spring .42 in-a preferred direction corresponding, as;.will;;be explai ned later, to a forward movement of the rearregister --to.;theright in Figure 2.; It

may likewise be operated in any manner desired,- by an .electrcmagnet, cam,or-fork,;for exarnple.

In the. -dia grams according to Figures 20 to 24 the folwi s qnxs t nnal ymbolsi av e 'used:

(1);The .,pipes,apd spaces covered, by doublecrossus in ra l qd-w h; fl i atth d scha g -p s ure of.

oasis/$55 (ZlThepipes and spaces covered by simplecrosshatching are filled with fluid at the pressure regulated by the control valve 24.

(3) The pipes and spaces covered by dots are filled with fluid at atmospheric pressure.

In order to attain a rapid forward movement of the.

with the ducts 43 and 44, and thecontrol valve 24 connects the ducts 32 and 33 to one another.

The whole output of the pump 30 arrivingat the distributor 31 through the pipe 36supplies the large chamber 45 through the pipes 43 and '46, and the small chamber 47 is in communication with the large chamber 45 through the pipes 48, 44, 43 and 46. The uniform pressure in the two chambers is accordingly identical, but as the piston has a greater surface in the large chamber 45 than in the small chamber 47, the resulting force on the piston 7 displaces the same towards the right. In its movement, the

piston 7 discharges'the fluid contained in the small chamber 47 through the pipes 48, 44, 43 and 46 into the large chamber 45.

The safety valve 39 being biassed by a'calibrated spring 49 in'such a maner as to keep the duct 36 closed at the normal pressure of the pump, the whole output of the pump 30 is used for supplying the cylinder 6 in a closed circuit. v

When the pressure in the duct 36 exceeds the normal control valve, the safety valve 39 opens and allows the excess output to return to the reservoir 29 through the pipe 40.

In the actuation of therear register it is always necessary to displace this register rapidly between the cuts, but the speed has to be reduced when approaching the end of the stroke in order to prevent any sliding of the material to be cut beyond the accurate point'at which the cut is to be made.

This reduction of speed is. attained by interrupting'communication between the duct 36 and the pipes 43 and 44 inthe distributor 31 (Figure 21). p

The pump can then supply the upper part of the circuit only through the throttle point 38.

This abrupt throttling would produce a strong increase in pressure in the lower part of the circuit if this pres sure" were not relieved by the safety valve 39.

The excess output of the pump 30 cannot pass through i the throttle point 38 and therefore returns to the reservoir 29 after passing through the safety valve 39.

The small mass flow of oil passing through the throttle point 38 supplies the large chamber 45, of the cylinder through the pipes 50 and 33, then through the control valve 24 and the pipes 32 and 46. V

The .small chamber 47 is in communication. with the large chamber 45 through the ducts 48 and 33, the control valve 24, and the ducts 32 and 46. The unitary pressure in the two chambers is equal, but the resulting force on the piston 7 pushes the same to the right, the oil contained in the small chamber 47 being discharged through the pipes 48, 33, 32 and 46 into the large chamber 45.

In order to stop the forward movement of the register 3 one may: I

(1) Displace in any desired manner the control valve 24 in order to interrupt the communication of the pipe-32 with the pipe 33. The total output of the pump 30 is returned to the reservoir 29 after having passed through the safety valve 39. r

(2) Displace in the preferred way illustrated in Figure 22 the control valve 24 in such a manner that it partly interrupts the communication between the ducts 33 and 32, and partly establishes communication between the ducts 32 and34, insucha manner-that the throttling points atmospheric pressure.

Sland 52 thus-set up by the edges of the valve 24 permits the passage of the output from the throttling member 38 through the valve 24 so as to return to the reservoir 29 through the pipe 34. a v

At that moment the chambers 45 and 47 are no longer supplied and the movement of the piston 7 and of the rear register 3 is stopped, the fluid circuit being in equilibrium.

An advantageous embodiment consists in stopping the register 3 by connecting it mechanically with the control valve 24 in arrested posit-ion. This connection may be established in such a way that the register in its forward movement always carrieswith it the control valve 24 in the direction of closing the throttle point 51 and opening the throttle point 52.

Thus the register advances slowly up to the momentwhen the position of the control valve 24 permits thereturn to the reservoir through the duct 34 of the total output of the throttling member 38 from the throttling points 51 and 52. The variation of the cross section area of the throttling points 51 and 52 being brought about by the forward movement of the register, this variation takes place progressively and the speed diminishes in a regular manner up to a complete standstill (Figure 22). This way of proceeding prevents the register from losing contact with the material to be in Figure 23) by actuating the control valve 24 in i such a manner that the 'duct 32 is connected to the duct 34'.

The output passing through the throttling member 38 supplies the small chamber 47 of the cylinder 6 through the pipes 50 and 48, while the large chamber 45 is put into communication with the reservoir 29 through the pipes 46 and 32, the valve 24 and the duct 34. The pressure in the large chamber 45 is accordingly equal to The piston 7 pushed by the oil at higher pressure in the small chamber 47 moves towards the left discharging the oil from the large chamber 45 which returns to the reservoir.

A' rapid rate of return of the register may be attained by actuating the distributor 31 in such a manner that the ducts 36 and 44 and. the ducts 43 and 53 are connected with one another, respectively, as shown in Figure 24.

The total output of the pump 30 supplies the small chamber 47 of the cylinder 6 through the pipes 44 and 48, while the oil from the large chamber 45 returns to the reservoir 29 through the pipes 46, 43 and 53.

When the rapid return movement comes to a standstill (Figure 22) the pressure rise is taken up by the safety valve 39. V

The means described hereinabove permit to obtain an automatic control of the rear register by using a follow-up device actuated in response to the position of the rear register and placing the slide valve 41 of the distributor 31 and the control valve 24 into the desired position.

' Follow-up device With reference to Figures 1, 2 and 3 it will be seen that the slider 16 carried along by the band 10 connected to therear register 3 by the bracket 5 and passing over the guide pulleys 11 to 15 can move on the track 17 fixed to the frame 1 of the machine.

As shown in Figure 4 the slider 16 carries a vertically movable finger -54; having at its.- lower end 55a .1 chamfo t 55 and :a notch a 56 i with-.a vertical. face; .on thefiank; the ,finger..54 and on its. upper .portionazcham-fer 57 provided for operating a micro-switchjsgbyithe inter mediary of a pusher--59. 5

h t r. 4,. w i hn s vb ase t o s lo e 'PQSiFiQQ y-t spring 60., ha al o Mo king-notch. 61 i tom h' h... a latch 62 can engage under the bias of a spring 615 said :latch actuating. a microsw-iteh 64.'=

A p rod 65 mou tedfi ra l e tiqa qpo i npaths underside of the slider;;16 is -;prpvided ;for disengaging e l hro th t h 6 e a tion o a sham: fer- 66 arranged oughe latch 2.

As o arr ed r' a ider 6. WEI ERMW":

draw the finger 54 upward.

h i i at; omm-ins azs atsdihae n he e, o. 6. r ta s. a QW .-.PQIF .r si u wer. w q; with a masnitr nsi a h h a ketin .1 9 ra a n den fa il t e. a

he s r. 5 a t-a a P 3 11593. 5.-: ov pp s .a series of abutments carried bythe barrel. 18.,

The barrel 18 ,is supported on the left hand side by a bearing 23 constituting a casing for the controlvalve 24 of the hydraulieeircuit. Thelcontrol valve 24 is qu r; a ,P g t r ia d.Pwg mh d s be uicklyreplaced: by other .dogs havingdifferent c0n1-,, aatio s. p i ad 931 5 3 1. n.-Xam ma sion. fixing thesedogs in position is given in Figure 4. The mi a at ne: m!.. fi s fl a ip in a am 2.9 1 i to. M011 2." rr gibr m b n.

rel 18.-

The other. end of the dog is pierced with a a hole 74 into which engagesthe point 75 of; a screw bolt 76 yin a-km ii q sadfi raw t a ho e' i the collar 77 of the abutment barrel, 45

The collars 73; and 77: have accordingly a groove 72 ifi 1 R 71. d. a 1 191 .7 r. ..=.s sw' ev s ive y. at @wh. P s ion-9 l e. abutms ts .e- 2e eight in the embodiment illustrated.

h bu m nt b en i 1'r .don .i e. ht n 50 side by a stub 78 sliding freely-in a bearing 79 of the support 25, and this; stub 78 .has on itsextension two chamfers 80 and sl -for actuating two micro-switches 82 and 83. A spring 42 biases thebarrel 18 and the control valve 24 constantly in a preferred direction to- 55 wards the right, and ,a pusher 84. held by a spring 85 which is stronger thanthe spririg 42 can limit the stroke of the barrel 18 by abutting on a cam 86;

This cam 86 can occupyalternately two positions under the control of an electro-ma gnetv 87 or of a spring 60 88 (Figures 6 and 7).

The cam 86 carries en an extension 89, a pawl. 90 engaging theteeth91 of a ratchet. wheel 92.: A 'spring 93Ibiases thepawl 190 into the teeth 91. By pulling on the-knurled knob 94. integral with the pawl 90 and by- 65 rotating it until a fingeri 95 engages in a notch 96 .of I the support 89,- the pawl 90 is' held disengaged from the teeth 91 of the ratchet wheeh92. (Figures 8 and 9).

A latch 97 biased by a spring 98 prevents any reverse rotationnoflthe .ratchet wheel. .92; 7O

Astar-shaped cam 99 (Figures-4, 10 and 11) fixedly.- connected to the ratchet .wheel.92.actuates..by the intermediary-of the cam faces 100 .and 101 and ofthe roller 102-,the. rocker. 103. oscillating about the axle Ra ion-. 2 otit e-a pporefieaad t. rries afing r bias by pring,;111.

of combiuations of.multiple dogs;70 to be mounted on the, barrel 18,. say eight in .wthe embodiment described: These holes 112 are.;.drille d, insuch a manner that a.-

linepfabutments isdisposed opposite the finger 54 when the roller ltlz is on anplevated-point v114 of the..canr. 99 When the r ller ;102, is on; an ;;adjacent 1 low point 115 of the.;carn 99, the line ofgabutment adjacent to the prece ding .one is opposite the finge1- 54.

Atknurled knob 116;;integral-,with the finger .110 per- Emits the disengagement. thereof from the collar 113 .in order to,allo.w the rotation ofthe .collar for the purpose of positioning any; desired gline -ofabutments opposite the. finger 54.

Figures-Maud. 5 show apart view of the machine provided with a manual control device. As can be seen.

in ,the,. drawing-the .guide pulley 11 for the band .10

maybe coupled--by. .a conicaljfriction clutch 11a with a ,worm. whet-1.111 by the action of-aspring 118. An.. electro-magnet 119 .declutches the. worm wheel 117 from. the pulley 11 when energised.

A worrn 129. meshes: with the. wormmwheel 117 and is re str.a ined ;from ,moyingaxially .with respect .to the.

abutments barrel-18 b means of, a .work 121.

A splined shaft 122 held axially in a bearing 123v integral 7 with. the; frame; ,1 .carries. .along. the. .worm

in rotation, but 4 leaves it.; free.. .fQr. translational 1 movement.

he. spl d s aft lllc nbe rotated. y a be el n nion 124 carried by the; slide. 16 and. slidable on -the "shaft;

The, slide 16 supports also. another bevelpinion 125 driven rotationally by, a hand wheel 126.. The. shaft 127 of the hand wheel 1261s freely slidableaxially with mieroswiteh 131 by displ acjng the hand wheel towards the right.

A ball 135 biased by. a spring 136 determines the axial positions of the shaft127 by engaging in the groove 13 0 or in the groove 134;

The operation of the follow-up device is as follows:

(1 Description, of a simple working cycle As a first'prerequisite -a rapid forward rate must be imparted-1o the rear register 3 between two cuts.

This-rapid forwardmovementis efiected by positioning the slide valve 41 'of' the distributor 31 as described heerinabove with reference to Figure 20.

The operation of the slide valve 41 in thedistributor 31 is effected in the following manner, with reference to Figure'4 and to the electric'twiring diagram Figure .25. Between two stopsthefinger 54 is free and biased by thespring 60,-andit finds itselfin the lower position While the micro-switch 58 is in the closed position.

The abutments barrel 18, biased by the spring 42, controls the micro-switch 82' by the chamferi 80, and closes the circuit The solenoid 137 vsets the slide valve 41. of-the distributor -31 into the I position for rapidforward 1' feed (Figure. 20.).

Whenthej;;materi alg to .;be cutarrives in; a position nearv ensae ainto a 1 0 .112. sin a col ar e abutments barrel 18 The .collar. 113 comprises as many holes 112 as is the possiblenurnber.

asse /st to a desired stop position, it is necessary to slow down the forward speed of the register in sucha manner that,

carried along by its own inerlia, the stack does not overshoot its normal position for the cut, losing contact with the register.

An abutment 19 is positioned for example in order to effect a stop at the desired point. When the chamfer 55 of the finger 54 comes into contact with the ridge 138 of the abutment 19, the reaction of the ridge 138 on the chamfer 55 lifts the finger 54. The chamfer 57 actuates the pusher 59 which controls the microswitch 58. The circuit being thus opened, the solenoid 137 is no longer energised, and a spring 148 restores the slide valve 41 of the distributor 31 to the neutral position. The supply can then take place only through the throttling member 38, and the register moves forward at a low speed (see Figure 21).

Thus a certain course is set up between the end of the rapid forward movement and the complete stoppage of the register.

If the material to be cut has a very low coefficient of friction, it is necessary to have a longer course between the end of the rapid forward feed and the complete stoppage of the register.

This longer course is obtained by placing before the stopping abutment 19 a cam 20 for slowing down the register over an appropriate length, the chamfer 140 of the cam 20 acting to raise the finger 54 which controls the opening of the micro-switch 58.

This position of the finger 54 is maintained during the whole of its course on the upper face 141 of the cam 20, and the feed takes place at a low speed. When the face 56 of the finger 54 comes into contact with the flank 139 of the adjacent abutment 19, the barrel 18 and the control valve 24 are carried along towards the left up to the moment when the control valve 24 stops the forward feed in the same manner as described hereinabove (Figure 22).

barrel 18 moves towards the right under the action of the spring 42, carrying along the control valve 24 which permits the slow feed of the rear register 3 and the slow movement of the slider 16 (Figure 21).

The micro-switch 82, actuated by the chamfer 80, closes and enables thus the solenoid 137 to be energised (Figure 25). When the end of the finger 54 leaves the upper face 143 of the abutment 19, the finger 54 drops under the bias of the spring 60, and the microswitch 58 closes the circuit of the solenoid 137, actuating the slide valve 41 of the distributor 31.

The register 3 moves consequently at a rapid rate of feed (Figures 20 and 25).

It should be noted that the register begins its forward movement at a slow rate. This peculiarity permits the finger 54 to come to a standstill with every safety on an 7 abutment very close to that which it has just left; this would not have been possible if the register had started off immediately at a high rate of feed.

In fact it needs a certain time for the finger 54 to descend. This time, although it is very short, allows a substantial displacement of the slider 16 if the feed begins at a high rate. In such conditions the finger 54 would invariably pass to the next adjacent abutment before descending.

The operation of stopping on an abutment and of advancing after a cut repeats itself until after the last cut provided in the program.

At this moment it is necessary to restore the reafregistei by the reaction of the chamfers 144 and 55, placed respectively on the cam 21 and on the finger 54, determines the raising of the finger.

In the first rising movement of the finger 54, the microswitch 58 opens the circuit of the solenoid 137. The feed takes place at a low speed (Figure 21) and the finger 54, always pushed by the chamfers 144 and 55 rises up to the moment when the notch 61 comes into line with the latch 62. The latch, biased by the spring 63, drops into the notch, and the micro-switch 64 closes the circuit of the solenoid 87.

The solenoid 87 rotates the cam 86 (Figures 6 and 7) so that the end 145 pushes the barrel 18 to the left in Figure 4 by the intermediary of the pusher 84 and of the spring 85. In order to perform a working cycle, the

finger 90 has to be disengaged from the teeth 91 (see Figures 8 and 9).

The barrel 18 carries along the control valve 24 into a position for slow return (Figure 23) and, when the chamfer 81 operates the micro-switch 83, the latter closes and energises the solenoid 146 which brings the slide valve 41 of the distributor 31 into the position for rapid return of the register (Figure 24).

When the push rod comes into contact with a cam 22 arranged on the barrel 18, the chamfer 147 of the cam 22 raises the push rod 65 which by the intermediary of the chamfer 66 disengages the latch 62 from the notch 61 of the finger 54.

The micro-switch 64 opens, and deenergizes the solenoid 87.

The cam 86 returns into a disengaged position under the action of the spring 88, and the abutments barrel 18 moves towards the right under the action of the spring 42 while the finger 54 has returned to its lower position under the action of the spring 60.

The distributor 31 is accordingly connected in such a manner as to effect a rapid forward feed (Figure 20).

The register 3 moves forward right up to the moment when the finger 54 meets an abutment 19 which determines the stopping in accordance with the procedure decessive movements of the latter have been renderedautomatic.

After the last out the register returns automatically to the starting position, ready to perform a new cycle of operations.

(2) Description of a complex operrzting'cycle It it is desired to apply the simple working cycle described hereinabove for cutting the four sides of a rectangular format, it suflices to dispose correctly on one of the grooves of the barrel four abutments as defined by v the marker 19.

(1) The register is in the position 1020 for the first cut.

(2) The operator pushes the stack into abutment with i the register and operates the first cutagain'ainto..zabutment Wit-h theregister, and':performs-,.=the.

second. cut;

(5); After the second cut the registersmovesautomatis.-

cally into the position 670:

(6),- ..The:..operator rotates; the stack this. time only '90? inmrdento bring itagainainto abutment with ..the.:register,-'

and the. third. cut is performed.

(7) 'Aftersthe -third: cut.v the. :registersrmoves automatically into :the position .650..for the fourtlrcut.

(8) The :operator.rotatesthe'stack again 180. After: the.;fourth.1cut:the. register :returns. automatically into; thee position 1020.

It willbe z-seen. accordingly .zthat'sfor cutting :four': faces oftz'theeformatrthe. operator.has. to' .turn: the pile twice:

180"; and. 'once 90?.

In order .to reduce the fatigue. ofzthe operator and the loss of timein handling,.it.wou1d be desirable .to. make the pile turn 90 only between cuts. For this purpose it.

would be nceessary to carry out the cutsin the sequence 1020-6701000 and 650.

In order to obtain this sequence it suflices to position the abutments1020and 670 on the line. A of the barrel. (Fig.

ures 27 and 28) and the abutments 1000 and650 on the. adjacent line B in such a manner thatthe lineA corre-.-

sponds to .the position of theforkrepresented in. Figures 10 and 12, and. the line B corresponds to .thezposition-rep-;. resented .-in Figures ,1 1 .and 13,; these: figures sh'owing.-.the..;.

details of the follow-up device.

Automatic return cams such as 21 are .positionedaheadi of stlrevlines A and 'B.:.while :cams22 forarresting of..the return movement are positioned behind them.

The knurled knob 94' is turned,':'the.finger.. 95:is:1lisengaged from the groove 96. and the-pawl .90 engages a:.

tooth 5.91'of the ratchet wheel 92 (Figure8).

The register is stopped at the position 1020 .for thefirstcut, the finger 54 being hooked on the stop 1020'line, A

(Figure12).

Afterthe first cut, the finger 54 willmove to the position .2

670.in the manner described hereinabove in the definition of-thesimple working .cycle, and the. stack 90?.

After the second cut in the position. .670 the .finger' 54- comes into contact with the adjacent cam 21 which by .the

intermediary 'of the chamfers 144 and '55 (Figure :4):'-

permits the latch 62..to drop into the groove .61,.thus energizing the solenoid 87. (Figures 6 and 7).

The solenoid 87 makes the cam 86 turn which effects the rapid return in the manner described hereinabove.- The pawl 90 which is fixedly connected to the cam-".86;

18'by thefinger 110 engaging in a hole 1120f the collar 113 rotates the barrel and brings the line B 'of abutments opposite thefinger 54 (Figure 13).

When the push rod 65 meets the cam 22 on the line B for stopping the return movement of the registen'the solenoid 87 is deenergized and the spring 88 restores'th'e cam 86' to -a disengaged position (Figure 6).

The disengagement of the cam 86 from the pusher 84 releases the barrel 1?: which under the actionof the spring 42 effects the rapid forward feed of the register and of the finger 54 right up to the abutment 1000.

The pawl -90 is disengaged from the tooth 91*ofthe ratchet wheel 02 and engages the next one, thiswheelzbeing held by the latch 97 under the action of the spring 98.5.

The operator rotates thestack 90 before proceeding .to the third cut.

operator rotates the After the @thirdjcutthei finger:54icomesrto a'stop on theabutment 650.:

The: operatorrrotates the pile again .90. and; makes the;

fourth .cutm.

Finally, after this last cut, the finger 54 meets-a return:

cam 21,-.whi'chienergizes the .solenoid87 in the. manner describ.ed:11ereinabove.

As before .thezenergizing of the, solenoid .87- rotates .the... cam-.86. so. as:.to effect. the rapid return, and thepawl The makes: the ratchet wheel-92 turnone pitch division.

cam:99.pushes the roller 102 by means of the chamfer. 101 to a high P08111011; The rocker 103 pivots on itsshaft. 104*andcarries theabutments barrel 18 along to position theiline Aofabutments opposite the finger 54 (Figure 12).

tooth .91 voffrhezwheel 92.1

The-.xbarrel; thus released-effects theforward feed of t the register 3 and of the slider 16. The finger-.54 moves forward and comesto a stop against the abutment.1020.

The register is nowin the operative position for a first cutofthe next stack of material.

(3) Operation of the manual control For cutting strips or standard formats, multiple dogprograms may be provided comprising as stated the combinationsof the various abutments or cams requiredfor the However, for certain special .op-.

work to be carried out.

erations-itrernains importantto be able to regulate manually= the positionof the. register ateach stroke: orto. ads. just-manually the position ofthe register. vandto place. an;

abutment'atthe point required.

For this kind of work the machine'is provided with a? device illustrated in the Figures 14,15 and 16, for discon-:

Figure-16, 'the micro-switch131is open; to deienergize solenoid 119. The spring v118 keeps the guideroller 611. of the band 10 engaged with the. worm wheel'117by the friction clutch 11a.

With-the register stopped the slide valve 41of the distributor 31 being in a neutral position. owing to the 7 action of thespring 148, and the control-valve 24 being in-the-stopposition at which the hydraulic circuit isin equilibrium (Figure 22), the guide'pulley *11'of the band 10 is fixed and so is the worm wheel 117 which is clutched to it.

The worm 120 is coupled by the fork 121 with the 9 abutments'barrel 13 and the control valve 24.

Thus a displacement of the worm'120 entails a corresponding displacement of the control valve 24-.

By turning the hand wheel 126 in one sense or the other, the worm 120is rotated by the pair of bevel gears 124 125 and the shaft 122.

When the Worm 120. reaches the fixed worm. Wheel 117, it moves axially and carries along the control valve 24 into a position effecting the slow movement of theregister (Figures 21 and 23) in the direction corresponding to the sense of rotation of the hand wheel 126.

As long as the rotation of the hand wheel 126' is continued, the worm .120 continues its axial displacement, and so does the valve 24 whichcontrols the movement.

When the rotation of the hand whee1126 is interrupted, the Worm wheel 117 driven by the pulley 11 and the band 10 attached to the register moves the worm 120 and the control valve24 until the latter reaches the position ofhydraulic equilibrium.

effecting a slow 'rnovement of the register being. very small, it suffices if the operator stops the rotation of:

the hand wheel126 at the moment. when the pointer 6 9 of themagnifyinglens .63 is in line with the. desired .POSltion on the scale 28.

When thefinger 54 comesinto contact with acam 22.3 onthe line A,.it deenergizes'the solenoid 87. 1 The (131111865 disengages itself, and the paw1-90-jurnps to the-next- The displacement of the control' valve necessary 'forassen ed Thus the operator can adjust the register manually and with accuracy to any desired stop position by advancing or retracting it by the hand wheel.

In the case when two desired stop positions are spaced apart quite considerably it would be tedious to effect the total movement of the register by turning the hand wheel.

With the hand Wheel 126 pushed inward (Figure 17), the chamfer 133 of the groove 130 energizes the solenoid 119 by closing the micro-switch 131 whereby the worm wheel 1170f the pulley 11 is released while the chamfer 128 energizes the solenoid 87 by closing the micro-switch 129.

The solenoid 87 effects the rapid return as described hereinabove by rotating the cam 86 until its corner 145 pushes the barrel 18 to close the switch 83 and energize the solenoid 146. As soon as the pressure on the hand wheel 126 is relaxed, the ball 135 biased by the spring 136 and bearing on the chamfer 133 restores the hand wheel 126 to its initial position at which the register is stopped (Figure 16).

With the hand wheel 126 pulled slightly outward (Figure 18), the chamfer 132 of the groove 130 energizes the solenoid 119 by closing the microswitch 131 which releases the worm wheel 117 from the pulley 11. The worm 120 thus released axially allows the barrel 18, which is loaded by the spring 42, to move the valve 24 into the position effecting a rapid forward feed by closing the switch 82 and energizing the solenoid 137 (Figure 20).

When the hand wheel 126 is released again the ball 135 biased by the spring 136 restores the hand wheel to its initial position of hydraulic equilibrium.

Thus the operator may effect the rapid forward or return movement of the register 3 and the'slider 16 by pulling or pushing slightly the hand wheel, or the slow forward or return movement of the slider 16 and the register 3 by turning the hand wheel. For rapid movement the hand wheel is moved in the same direction as the register, and for slow movement in the same direcaxially by abolishing the connection of the pulley 11 with v the worm wheel 117.

For this purpose the hand wheel is pulled out all the way until the groove 134 comes into line with the ball 135 and the micro-switch 131 (Figure 19). This groove being less deep than the groove 130, it keeps the microswitch 131 in a position energizing the solenoid 119.

Finally, in case the immediate stopping of the rear register in the course of an automatic Working cycle is required, the hand wheel 126 is pushed in so as to restore the same to its initial position.

It will be readily appreciated from the foregoing de scription of the invention, in its particular application to driving, and controlling the movements of, a paper gullotine register, that the hydraulic circuit, follow-up mechanism and manual control system of the invention are susceptible of being applied individually or in their entirety to any machine having a moving part, the movements of which must be controlled for rapid rate or slow.

rate and accurately stopped at predetermined positions. Thus the scope and spirit of the invention includes all machines and apparatus falling within the ambit of the appended claims, without any limitation to the specific example herein described.

What is claimed is:

. 1. A hydraulic drive and control device comprising a source of fluid at constant pressure; a fluid circuit including a pressure branch connected to the source and a return branch at low pressure; throttling means in the pressure branch restricting the rate of fluid flow therethrough; a fluid motor having a low power side permanently connected to the pressure branch downstream of the throttling means and a high power side; control means having a first connection to the low power side of the.

motor, a second connection to the high power side, and a third connection to the return branch, by-pass means with connections respectively to the pressure branch upstream and downstream of the throttling means, to the return branch, and to the high power side of the motor; and valve means for controlling the connections of the by-pass means.

2. A hydraulic device as in claim 1 wherein the valve means comprise a slide-valve having three operative positions at which, respectively, in the first position the pres-- sure branch upstream of the throttling means is connected to the high power side of the motor and to the pressure branch downstream of the throttling means for direct supply of fluid from the source to both sides of the motor, in the second position the by-pass means is closed to fluid flow therethrough, and in the third position the pressure branch upstream of the throttling means is connected to the pressure branch downstream of the throttling means for direct supply of fluid to the low power side of the motor and the high power side is connected to the return branch.

3. A hydraulic device as in claim 2 comprising a spring biassing the slide-valve into the second position, and means for actuating it into each of the other two positions.

4. A hydraulic drive and control device comprising a source of fluid at constant pressure; a fluid circuit including a pressure branch connected to the source and a return branch at low pressure; throttling means in the pressure branch restricting the rate of fluid therethrough; a fluid motor having a low power side permanently connected to the pressure branch downstream of the throttling means and a high power side; and control means having a first connection to the low power side of the;

nections thereof are in communication for metered flow of fluid therethrough to both sides of the motor and to the return branch, and in the third position the first connection is closed and the second and third connections are in communication to connect the high power side of the motor to the return branch.

5.A hydraulic device as in claim 4 further comprising a mechanical connection between the motor and the feeler valve, and means biassing the feeler valve toward the first position.

6. A hydraulic device as in claim 4 further comprising by-pass means with connections respectively to the pressure branch upstream and downstream of the throttling means, to the return branch, and to the high power side of the motor; and valve means for controlling the con nections of the by-pass means.

7. A hydraulic device as in claim 6 wherein the valve means comprise a slide-valve having three operative positions at which, respectively, in the first position the pressure branch upstream of the throttling means is connected to the high power side of the motor and to the pressure branch downstream of the throttling means for direct supply of fluid from the source to both sides of the motor, in the second position the by-pass means is closed to fluid flow therethrough, and in the third position the pressure branch upstream of the throttling means is connected to the pressure branch downstream of the throttling means for direct supply of fluid to the low power side of the motor and, the high power side is connected to the return branch.

8. A hydraulic device as in claim 6 comprising a spring biassing the slide-valve into the second position, and means for actuating it into each of the other two positions.

9.5-A-hydraulic; delviceas in claim4 further comprising aimechanical;connection. between the motor and the feeler-valve; means, biassing the feeler valve toward the third position, by-pass'means with connections respectively-tothe pressure branch upstream and downstream of the throttling means, tothe return branch, and

to the high power side of the motor; and valve meansfor.

controlling the connections of the by-pass means 10.,A hydraulic device as in claim 9 wherein the valve 1 cans comprise a slide-valve having three operative positions at which, respectively,in the first position the pres-- sure branch upstream of the throttling means is con-- nected to the high power 'side of the motor and to the pressure branch downstream of the throttling means for direct'supplyof fluid from: the source to both sides of closed to fluid flow therethrough, and in the third 'posi-' tion the pressure branch upstream of the throttling means the motor, in the second position the by-passmeans 'is is connected to the pressure branch downstream-of the I throttling means for direct supply of fluid tothe-low power side of the motor and the high power side is connected to the return branch.

11. A hydraulic device as in claim 10 comprising a-spring biassing the slide-valve into the second position, and means for actuating it into each of the other connected to the pump; a meteredcircuit connecting the supply branch'to both chambers; a free circuit connecting the supply'branch to. both chambers; a return branch 'connccting each circuitto exhaust; first control-means inserted in the metered circuit and connected to the free circuit.

for determining the direction of movement of the piston between the two chambers and for stopping the pistonin adjusted position; and second control means insertedin the free circuit for selectively'opening the freecircuit to by-pass the metered circuit, closing the free circuit,.and connecting the free circuitto-the small chamber andthe return branch to the large chamber.

13. A hydraulic device as in claim 12 further comprising a follow-up mechanism connecting the pistonzto the first control means-foractuating the latter in:dependence on the position of the former.

14-. A hydraulic device as in claim 13 wherein the first control means comprises a feeler valve; .and the follow-up mechanism comprises an indexing finger conconnection between the drum and feeler valve for joint movement.

15. A hydraulic device as in claim l4 comprising a slide-movable along said path and supporting the finger.

for movement toward and away from the drum; means for retracting the finger from a normal position in said path; a latch for retaining the finger in retracted posi-.

tion; and means extendingfrom the slide into said path:

for releasing the latch.-

16. A hydraulic device as in claim 15 further compris-= ing'an electrical control circuit; electromagnetic means fo'r actuatingthe second control means; a pair of normally open switches inserted in the control circuit and actuatable alternately by'the drum to energize the electromagnetic means and actuate the second control means to connect the free circuit selectively either to both cylinder chambers or only to the small chamber with the large chamber connected to t the return branch; a normally closed switch inserted in the control circuit in series with 16 oneyofthepairofswitches; and means on the slide for opening the normally closed switch with the finger retracted.

17. A hydraulic device as in claim 16 further comprising means limiting movement of the drum in said preferred direction selectively at two end positions; an electromagnetindexing thev limiting means at said two positionsr asfurther normally open switch inserted in the control circuit; and switch actuating means connecting the latch to thefurther switch to energize the.electromagnet with the fingerretained by the latch.

18. A hydraulic drive and control device comprising. a -fiuid circuit; a-constant output pump in the circuit; a

motor in :the circuit having a work stroke anda return: strokeya throttled'branch in the circuit connected to the motor to determine slow rate movement of the motor; a1 control" valve in the circuit to determine direction of" movement of the motor and equilibrium of .the circuit for stopped condition; a by-pass around :the throttled branch to determine rapid rate movement of the motor,

and a follow-upzmechanism" connecting vthe; motor to the control valve; and manual control means in the follow-up mechanism operative selectively with the circuit in equilibrium to actuate the control valve for monitored slow rate movement-of the motor in either directionand to actuate the .control' valve and the by-pass for monitored rapidrate movement in either direction.

19., A hydraulic device. as in claim .18. comprisingta hand wheel having a disengaged position, a slow rate position, and rapid rate positions respectively for work and return strokes; a clutch and transmission coupling the hand wheel to the follow-up mechanism with vthe circuit in equilibrium and the hand wheel in slow rate position; and electromagnetic means controlling the by-passwith the hand wheel in rapid rate positions.

20. 'In a machine having a motor with a work stroke and a return stroke, a hydraulic circuit for energizing the motor,-*a constant feed source supplying the circuit, and control means in the circuit for effecting slow rate and rapid rate actuation of the motor and for stopping the motor at any desired point of either stroke: a follow-up mechanism comprising a slide movable with the motor along a predetermined path; a function drum positioned alo'ng'said path and operatively connected to the control meansg a retractible finger mounted on the slide to contactthe drum, means for mounting on the drum a plurality of function dogs spaced around the periphery thereofiindexing means for rotating the drum to bring a desired dog into said path; and means operable .by the finger" to-actuate the indexing means.

21. ha machine having a motor with a work stroke and a return stroke, a hydraulic circuit for energizing the motor, "a constant'feed source supplying the circuit,-and control means in the circuit for effecting slow rate and rapid rate actuationof the motor and for stopping the motor at any desired point of either stroke: a follow-up mechanism comprising a slide movable with the motor along a predetermined path; a function drum positioned alongsaid pathrand operatively connected to the control means; and a retractible finger mounted on the slide to contactthe drum, comprising a drum-contacting tip havinga chamfer at the leading edge thereof in the direction of .the work stroke and a notch following the chamfer and having a wall substantially perpendicular to the path of movement.

22. A follow-up mechanism as in claim 21 comprising means supporting the drum for limited axial movement; and. means normally biassing the drum to actuate the control means in the, direction of work stroke.

23. Arfollow-up mechanism as in claim 22 comprising an abutment on the drum positioned to engage the cham-,

fer on the finger tip and to cam the finger toward partly retracted position; and actuating means on the slide operable by the partly retracted finger to actuate the control =means from rapid rate to slow rate.

24. A follow-up mechanism as in claim 20 wherein the finger comprises a drum-contacting tip having a chamfer at the leading edge thereof in the direction of the work stroke and a notch following the chamfer and having a wall substantially perpendicular to the path of movement.

25. A follow-up mechanism as in claim 24 comprising means supporting the drum for limited axial movement; and means normally biassing the drum to actuate the control means in the-direction of return stroke.

References Cited in the file of this patent UNITED STATES PATENTS Whitesell Sept. 13, 1932 Burrell May 16, 1933 Barnes Aug. 27, 1935 Strawn June 6, 1939 Vickers Feb. 10, 1942 Price Oct. '23, 1951 

